Annular seal

ABSTRACT

A seal assembly capable of low temperature service is disclosed. It features upper and lower metallic backup rings that are specially shaped to act as a spring to keep the sidewalls of such rings in contact with the inside and outside surfaces to be sealed to prevent extrusion of the seal material even in low temperature situations. Inner and outer grooves are provided. O-ring seals, used for the ID of the seal, are manufactured to have a slightly greater diameter than the groove into which they will be installed. The greater length provides stored energy to promote sealing functionality in cold temperature situations. The O-rings used for the OD of the seal are manufactured to have a slightly smaller diameter than the groove into which they will be installed. The shorter length provides stored energy to promote sealing functionality in cold temperature situations.

RELATED APPLICATIONS

This application is a Continuation of application Ser. No. 13/568,072,filed Aug. 6, 2012, entitled “Annular Seal” in the name of Kendall E.Keene et al., which is a Continuation of application Ser. No.12/819,098, filed Jun. 18, 2010, entitled “Annular Seal” in the name ofKendall E. Keene et al., which is a Continuation of application Ser. No.10/664,747, filed Sep. 18, 2003, entitled “Annular Seal” in the name ofKendall E. Keene et al., each of which is hereby incorporated byreference in its entirety for all purposes.

FIELD OF THE INVENTION

The field of this invention is sealing annular spaces in wellhead ordownhole applications and, more particularly, where low temperatureexposure to the seal assembly is anticipated.

BACKGROUND OF THE INVENTION

Seals for annular spaces in downhole applications have to respond to avariety of changing conditions. During production, the produced fluidscan raise operating temperatures to 350° F. or more. On the other hand,particularly in frigid climates and during shut in periods of noproduction, the surrounding temperature around a wellbore seal canplunge to 35° F. or even less. Traditional annular non-metallic sealdesigns employ anti-extrusion barriers on the top and the bottom. Thesedevices or rings often follow the generally rectangular shape of theseal, when viewed in section. The backup rings have a generally U-shapeand feature slight interference on the inside diameter and moresignificant interference on the outside diameter, as installed. Anexample of the generally U-shaped design for the anti-extrusion ring inan annular seal can be seen in U.S. Pat. No. 4,496,162. In a variationof this design, additional seal material has been added to the insidedimension of the seal assembly to make a portion of the seal protrudebeyond the backup rings on the inside diameter dimension. Even though anincrease in the inside diameter interference reduced failures at lowtemperatures, the prior design proved unreliable in exposure to evencolder temperatures as experienced in shut in conditions in the harshestcold climates. Additionally, the increase in inside diameterinterference made the seal significantly more difficult to install.Compression packer seals are generally illustrated in U.S. Pat. Nos.:1,350,553; 3,229,767; 3,554,280 and 4,326,588.

In the present invention, installation interference that activates theseal is generated by the relaxed OD of the seal being larger than the ODof the annular gap the seal is being installed in and the relaxed ID ofthe seal being smaller than the ID of the annular gap the seal is beinginstalled in. The seal does not rely of any external axial load tofunction. The seal is assisted by pressure during normal functionality.

Accordingly, the present invention presents improvements to seal designto handle the colder environments. In one feature, the backup ringdesign has been revised to allow it to act as a spring to promote itsability to act as an extrusion barrier. In another development,resilient ring seals have been placed in the seal body and dimensionallyconfigured to be installed in their respective grooves with a residualstored force to promote the operation of the seal assembly in reducedtemperature environments. These and other features of the presentinvention will be more apparent to those skilled in the art from areview of the description of the preferred embodiment and the claims,which appear below.

SUMMARY OF THE INVENTION

A seal assembly capable of low temperature service is disclosed. Itfeatures upper and lower metallic backup rings that are specially shapedto act as a spring to keep the sidewalls of such rings in contact withthe inside and outside surfaces to be sealed to prevent extrusion of theseal material even in low temperature situations. Inner and outergrooves are provided. O-ring seals, used for the ID of the seal, aremanufactured to have a slightly greater diameter than the groove intowhich they will be installed. The greater length provides stored energyto promote sealing functionality in cold temperature situations. TheO-rings used for the OD of the seal are manufactured to have a slightlysmaller diameter than the groove into which they will be installed. Theshorter length provides stored energy to promote sealing functionalityin cold temperature situations.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a sectional view of the preferred embodiment of the presentinvention.

FIG. 2 is a view of a ring such as 30 along lines 2-2 of FIG. 1 showingthe undulating wave pattern.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT

The seal of the present invention is shown in FIG. 1. The seal has abody 10 and an upper backup ring 12 and a lower backup ring 14. The ring12 may be formed of metal or plastic. The preferred embodiment is metal.The details of ring 12 will be described with the understanding that thepreferred embodiment uses an identical ring 14. The invention does notrequire identical rings 12 and 14 and is functional with only one ofsuch rings. Ring 12 features inwardly looping ends 16 and 18 that can besnapped onto the body 10 in a gripping engagement under a residualforce. In essence, the upper end 20 of the seal body 10 is subjected toa compressive force by the ends 16 and 18. At the same time, the ends 16and 18 are forced into an interference fit in the annular gap in whichthe seal is disposed. The ring 12 has a bend 22 that absorbs and storesa force as ends 16 and 18 are pushed into the interference fit of theannular space in which they are mounted. As a result, ring 12 acts as aspring due to the placement of bend 22. This spring effect pushes theends 16 and 18 away from each other and into contact with the opposingwalls that define the annular space that the seal assembly is intendedto close. Installation of the ring 12 into the annular space causes itto elastically deform while transferring potential energy into bend 22.By design, the bulk of the bending by installation of the seal assemblyoccurs at bend 22. The ring 12 may be shaped to allow pressure toenhance or diminish the energy stored in the bend. The shape of the ring12 may also be used to control the amount of force, generated bypressure, that is passed through to the body 20.

The body 10 can be made of a plastic or an elastomeric material having aDurometer hardness of preferably about 85 to 90 and optionally withreinforcement of preferably glass or carbon fibers. Alternatively,reinforced PTFE can be used. The body 10 comprises grooves 24 and 26that respectively hold ring seals 28 and 30. Additionally, grooves 32and 34 respectively retain ring seals 36 and 38. Body 10 adds support torings 12 and 14 and acts to force the rings out to prevent extrusion.The grooves can be square cut, dovetailed or round bottomed. The latterform is preferred due to its ability to provide a more nearly volumefilled arrangement.

Rings 30 and 38 are the main sealing members. Optionally, only one ringcan be used on the outside diameter or more than two rings. Thepreferred material is about a 65 to 85 Durometer Arctic Nitrile toenhance low temperature performance. In the preferred embodiment, thereis radial interference on rings 30 and 38 when installed in the annulargap to be sealed. Interference in the range of about 20-25% of thediameter of the ring 30 or 38 is preferred, with a minimum interferenceof at least about 0.015 inches. This configuration minimizes diametralstretch. Additionally, rings 30 and 38 are preferably shorter incircumference than their respective grooves 26 and 34 by about 6-20% tobetter retain them in the grooves for insertion into the annular spaceand during operation, particularly in lower temperature conditions.

With regard to inside diameter rings 28 and 36, it is preferred thatthey be sized so that they are circumferentially compressed wheninstalled into their respective grooves 24 and 32. A circumferentialcompression in the range of about 8-15% of the relaxed circumference ispreferred. This is achieved by making the circumference of rings 28 and36 about 8-15% longer than the groove into which it is to be mounted.The larger the oversize, with the rings still in their respectivegrooves, the greater is the force against backup rings 12 and 14 and, inturn, the greater is the stored force in rings 12 and 14 to force theends, such as 16 and 18 against the inner and outer surfaces that definethe annular gap that the seal assembly is meant to close. The preferredmaterial is about a 65 to 85 Durometer Arctic Nitrile to enhance lowtemperature performance. When rings 28 and 36 are installed and incontact with the inside diameter the circumferential compression resultsin an axial wave pattern occurring in the respective groove as well assome pushing of grooves 24 and 32 toward grooves 26 and 34 respectively.This wave deformation in the axial direction along the circumferenceputs an additional axial force against rings 12 and 14 to cause theirrespective ends, such as 16 and 18 to splay apart for better contactwith the walls that define the inner and outer surfaces to be sealed bythe seal assembly.

While the seal assembly has been illustrated for use in a staticcondition, the design is workable in a dynamic situation. Those skilledin the art will appreciate that the seal assembly can be mounted forsupport in a groove in the inner 13 or outer body 15 forming the annulargap 17 that the seal assembly is designed to close. The backup rings 12and 18 can be optionally used without the seal rings 28, 30, 36, and 38.FIG. 2 shows the undulating profile viewed in the axial direction afterassembly of one of said rings to an associated groove. Alternatively anynumber of seal rings can be used on the inside or the outside diameter.Alternatively, one or more seal rings in groove can be used only on theinside or the outside diameter, within the scope of the invention.

The foregoing disclosure and description of the invention areillustrative and explanatory thereof, and various changes in the size,shape and materials, as well as in the details of the illustratedconstruction, may be made without departing from the spirit of theinvention.

1.-25. (canceled)
 26. A seal assembly for sealing an annular spacebetween first and second bodies, comprising: an annular body havingfirst and second ends, wherein the annular body comprises at least onenotched portion disposed between the first and second ends; and at leastone ring disposed on one of the first or second ends, the ringcomprising: a pair of loop ends extending toward the annular body andconfigured to secure the ring to the annular body; and an inflectedportion located between the loop ends and in abutment with the annularbody, wherein the inflected portion facilitates elastic deformation ofthe ring.
 27. The seal assembly of claim 26, wherein the inflectedportion is configured to absorb forces when the pair of loop ends areforced into the annular gap between the first and second bodies.
 28. Theseal assembly of claim 27, wherein the pair of loop ends are configuredto bias away from each other due at least in part to the forces absorbedby the inflected portion.
 29. The seal assembly of claim 26, wherein thepair of loop ends are generally u-shaped, and the inflected portion isgenerally v-shaped.
 30. The seal assembly of claim 26, comprising afirst sealing ring disposed in a first notched portion of the annularbody and configured to provide a biasing force in a radially inwarddirection with respect to the annular body.
 31. The seal assembly ofclaim 30, wherein the first notched portion comprises a bottom and afirst circumference at the bottom, wherein a second circumference of thefirst sealing ring at a location nearest the first circumference of thefirst notched portion is configured to differ before mounting from thefirst circumference of the first notched portion to provide a net radialforce to the annular body.
 32. The seal assembly of claim 31, whereinthe second circumference of the first sealing ring is at leastapproximately 8 percent different from the first circumference of thefirst notched portion in which it is installed.
 33. The seal assembly ofclaim 31, wherein the annular body comprises a second sealing ring in asecond notched portion disposed on an opposite side of the annular bodyfrom the first sealing ring, wherein the second sealing ring isconfigured, when the annular body is installed in the annular gapbetween the first and second bodies, to form an interference fit withone of the first and second bodies to an extent of at leastapproximately 20 percent of the cross-sectional diameter of the secondsealing ring.
 34. The seal assembly of claim 26, wherein the annularbody comprises a longitudinal axis, and the pair of loop ends extendradially toward one another relative to the longitudinal axis to gripthe annular body.
 35. The seal assembly of claim 26, wherein the pair ofloop ends continuously extend toward one another.
 36. A seal assemblyfor closing off an annular gap between a first and second body andsupported by at least one of the first and second bodies, comprising: anannular body having an upper and a lower end and a longitudinal axis,wherein the annular body comprises a first groove having a bottom and afirst circumference at the bottom; and at least one ring mounted on oneof the ends of the annular body and configured to have a relaxeddimension greater than the annular gap between the first and secondbodies so that opposed loop ends on the ring are compressed to beinserted in the annular gap, the ring comprising a bend between theopposed loop ends configured to store a force created by insertion ofthe ring into the annular gap and to apply the force on the opposed loopends against the first and second bodies.
 37. The seal assembly of claim36, wherein the opposed loop ends are configured to bias away from eachother due at least in part to the forces stored by the bend.
 38. Theseal assembly of claim 37, wherein the opposed loop ends are generallyu-shaped, and the bend is generally v-shaped.
 39. The seal assembly ofclaim 36, wherein the annular body comprises at least one first ring inthe first groove, wherein a second circumference of the first ring at alocation nearest the first circumference of the first groove isconfigured to differ before mounting from the first circumference of thefirst groove to provide a net radial force to the annular body.
 40. Theseal assembly of claim 39, wherein the first ring is configured tocontact the one of the first and second bodies with the largerdimension; wherein the first ring is configured, when the annular bodyis installed in the annular gap, to form an interference fit with theone of the first and second bodies to an extent of at leastapproximately 20 percent of the cross-sectional diameter of the firstring.
 41. The seal assembly of claim 39, wherein: the annular bodycomprises at least one second ring in a second groove disposed on anopposite side of the annular body from the first ring; the second ringis configured to contact the one of the first and second bodies with thelarger dimension; and the second ring is configured, when the annularbody is installed in the annular gap, to form an interference fit withthe one of said first and second bodies to an extent of at leastapproximately 20 percent of the cross-sectional diameter of the secondring.
 42. The seal assembly of claim 39, wherein the first ring issofter than the annular body.
 43. The seal assembly of claim 39, whereinthe first ring is configured, when placed in contact with one of thefirst and second bodies, to deform the first groove to force the opposedloop ends of the ring away from each other, and in response to thedeformation of the first groove the first ring is configured to deforminto an undulating wave pattern in an axial direction parallel to thelongitudinal axis.
 44. The seal assembly of claim 36, wherein theopposed loop ends extend radially toward one another relative to thelongitudinal axis to grip the annular body.
 45. A seal assembly forsealing an annular gap between first and second bodies, comprising apair of rings on first and second ends of an annular body; wherein eachring comprises a pair of u-shaped loops extending radially toward oneanother radially into the annular body and securing the ring to theannular body; wherein each pair of u-shaped loops are connected by av-shaped bend that facilitates elastic deformation of the ring; andwherein the annular body comprises a plurality of rectangular grooves onsides of the annular body between the pair of rings.